CA2761841A1 - Grinding device for rollers - Google Patents
Grinding device for rollers Download PDFInfo
- Publication number
- CA2761841A1 CA2761841A1 CA2761841A CA2761841A CA2761841A1 CA 2761841 A1 CA2761841 A1 CA 2761841A1 CA 2761841 A CA2761841 A CA 2761841A CA 2761841 A CA2761841 A CA 2761841A CA 2761841 A1 CA2761841 A1 CA 2761841A1
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- Prior art keywords
- grinding device
- roller
- grinding
- carriage
- guide rails
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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- 238000000227 grinding Methods 0.000 title claims abstract description 139
- 239000000123 paper Substances 0.000 claims abstract description 14
- 238000004381 surface treatment Methods 0.000 claims abstract description 4
- 230000033001 locomotion Effects 0.000 claims description 26
- 239000000523 sample Substances 0.000 claims description 22
- 238000013016 damping Methods 0.000 claims description 7
- 230000005284 excitation Effects 0.000 claims description 4
- 239000000969 carrier Substances 0.000 claims description 3
- 238000009413 insulation Methods 0.000 claims description 2
- 230000003134 recirculating effect Effects 0.000 claims description 2
- 238000012545 processing Methods 0.000 abstract description 4
- 238000000034 method Methods 0.000 description 12
- 238000005259 measurement Methods 0.000 description 7
- 238000004049 embossing Methods 0.000 description 5
- 238000009434 installation Methods 0.000 description 4
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B24—GRINDING; POLISHING
- B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
- B24B5/00—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor
- B24B5/36—Single-purpose machines or devices
- B24B5/37—Single-purpose machines or devices for grinding rolls, e.g. barrel-shaped rolls
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B24—GRINDING; POLISHING
- B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
- B24B41/00—Component parts such as frames, beds, carriages, headstocks
- B24B41/02—Frames; Beds; Carriages
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B24—GRINDING; POLISHING
- B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
- B24B49/00—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation
- B24B49/12—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation involving optical means
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B24—GRINDING; POLISHING
- B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
- B24B5/00—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor
- B24B5/36—Single-purpose machines or devices
- B24B5/363—Single-purpose machines or devices for grinding surfaces of revolution in situ
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Grinding Of Cylindrical And Plane Surfaces (AREA)
- Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
- Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
Abstract
The invention relates to a grinding device (1) for the surface treatment of rolls (2), particularly of rolls (2) for machines producing, finishing and/or processing webs, such as paper, cardboard or tissue machines, comprising stationary components and mobile components which can be separated from each other. The stationary components comprise guide rails (5), which extend substantially in parallel to a roll axis of the roll (2) to be treated and which are connected to a subsurface (6). Thus, the stationary components, such as the guide rails (5), can remain at the place of use of the rolls, while the components that are mobile or can be transported can be easily separated from the stationary components and can be transported to other locations.
Description
Grinding device for rollers The invention relates to a grinding device for grinding rollers, in particular for grinding rollers for machines for producing and/or finishing a web of fibrous materials such as, for example, a web of paper, cardboard or tissue, as claimed in the preamble of claim 1.
The rollers which are used in the paper industry are subject to unavoidable wear. The re-processing is at present usually carried out by transporting the rollers to a service centre and conditioning them there.
However, since the dimensions and the weight of these rollers are continuously increasing - over 100 t weight and 12 m length are no longer unusual - an alternative concept is both economically desirable and necessary, for example due to restrictions on goods traffic. A
grinding device which is mobile and can be easily transported to a paper factory and operated there is suitable for this.
A device and a method for grinding roller surfaces which are described in WO 01/49451 Al are already known for dry cylinders of paper machines for producing tissue paper. The dry cylinders in this type of paper machine are, on the one hand, very large and, on the other hand, are difficult to disinstall due to their heatable configuration, for which reason the surface of the so-called yankee cylinders always have to be treated in situ. WO 01/49451 Al describes a grinding device for grinding such a yankee cylinder, wherein the grinding device which can be moved in a direction which is essentially parallel to the roller and can be displaced toward and away from the roller. Furthermore, a measuring system which is assigned to the grinding device and can be moved therewith is provided for measuring the roller, relative to at least one reference line which is provided outside the roller and is adjusted parallel to the axis of the roller, wherein the relative position is determined in a plane which is preferably perpendicular to the reference line. The grinding process which is carried out by the grinding device, i.e. the contact pressure force or the contact pressure, is regulated on the basis of the measured values which are obtained by the measuring system. The grinding process therefore takes place with force control on the basis of a previous measurement of the surface.
A disadvantage with this known grinding device is here, on the one hand, that the measuring system does not reach the level of accuracy which is required for treating roller surfaces with various coverings, and the force-controlled grinding is difficult with soft or elastic coverings. The yankee cylinders which are mentioned further above are made of metal or are provided with a ceramic coating or hard metal coating, but are not covered with a soft covering.
In addition the suitability of the belt grinding technology, used according to WO 01/49451 Al, for treating soft roller coverings is not provided to the desired degree.
Furthermore, the guide which is used in the device known from WO 01/49451 Al, on the scraper bar, is not available, and said device would also not be suitable for grinding with geometric guidance.
Conventional grinding machines, such as are known, for example, from EP 1 584 396 A, have the disadvantage of being entirely secured to one location. This is due, in particular to the formation of the grinding beds for these grinding machines. Such grinding beds usually comprise in this context a concrete square of large dimensions and mass, which is arranged in a suitable recess in the substructure, for example of a hall, and is mounted on springs for decoupling oscillation. Such a grinding bed can weigh several hundred tonnes and therefore can be manufactured only at extreme cost. In addition, such a grinding bed runs contrary to any requirement for mobility. Grinding machines with such a grinding bed are built exclusively for stationary use and cannot be transported.
Accordingly, the object of the invention is to specify a grinding device for rollers which is mobile, does not require a costly and heavy grinding machine bed and is suitable for use with any desired roller surfaces.
In this context, important criteria are the requirements for accuracy and the unsusceptibility to faults as well as the coverage of a wide application field.
According to the invention, there is the provision that the grinding device comprises stationary components and mobile components which can be separated from one another, and wherein the stationary components comprise guide rails which extend essentially parallel to a roller axis of the roller which is to be treated and are connected to a substructure.
The stationary components move here within a framework which is distinguished, in comparison with normal grinding beds, by ease of installation, small requirement for foundations and cost-effectiveness. The stationary components can therefore be present in any paper factory which desires them, while the mobile components can be easily distanced from the stationary components, and the mobile components can then be moved to other locations in order to be used there.
Paper factories are therefore neither forced to set up a separate, very costly stationary grinding device, nor must heavy and long rollers be sent to a service centre at enormous cost. The acquisition of the mobile components is also dispensed with since they can be ordered, used and transported away again as required in the form of a service performance. The cost factor for fixed installations is therefore low.
Further advantageous aspects and refinement variants can be found in the dependent claims.
The guide rails can be advantageously connected directly to the substructure with carriers which are inserted into the substructure or with a frame which is inserted into the substructure, with the result that a foundation arrangement which corresponds to the required accuracy levels can be achieved.
The roller which is to be ground can preferably be arranged on bearing blocks which are connected to the substructure.
In order to decouple the bearing blocks and/or the guide rails, passive insulation against excitation of vibrations in the form of a damping layer and/or damping elements in the form of spring elements can be provided between the substructure and the bearing blocks and/or between the substructure and the guide rails.
The bearing blocks and/or the guide rails can also particularly preferably have devices in the form of actuators which can be open-loop and closed-loop controlled, for actively bringing about decoupling from the substructure. This is a costly but very reliable form of damping. Mixed forms composed of active and passive damping are also possible.
In order to permit both large and small roller diameters to be treated and to be able to set the position of the tool for surface treatment correctly with respect to the roller axis, it is advantageous if the bearing points of the roller in the bearing blocks are both horizontally and vertically adjustable.
Mobile components of the grinding device can advantageously comprise a longitudinal carriage which is movably guided on the guide rails and is arranged in such a way that it can be moved or slid along an extension direction of the roller axis of the roller which is to be treated.
The longitudinal carriage can preferably have bearings which interact with the guide rails. Preferred forms of bearing are in this context sliding bearings or roller bearings. A particularly preferred embodiment provides here for the formation of a fixed/freely moving bearing with the circulating roller shoes which have a high degree of accuracy and good guidance with little susceptibility to offsets in the transverse direction with respect to the direction of movement.
Preferably a transverse carriage is arranged so as to be movable or slidable on the longitudinal carriage, wherein a movement direction of the transverse carriage is oriented essentially perpendicularly to the movement direction of the longitudinal carriage. As a result, the desired means of freedom in the movement relative to the roller can be actuated directly and in a simple way.
In order to be able to carry out specific embossing or form other surface structures in the roller surface, it is also advantageous if the transverse carriage can be horizontally and/or vertically pivoted with respect to the longitudinal carriage.
A rail bearing system can also be formed between the longitudinal carriage and the transverse carriage, which rail bearing system can be embodied in such a way that, in particular, bearings engage around guide rails since as a result it is possible to provide protection against lifting-off forces during the processing.
The transverse carriage can be arranged in such a way that it is secured on the longitudinal carriage or can be removed therefrom. A secured arrangement facilitates the expenditure on mounting since the transverse carriage does not have to be specially mounted, and on the other hand a removable transverse carriage contributes to the compactness of the device.
A tool, in particular a grinding disk, a belt grinder, a grooving device, a superfinishing device or a honing device can advantageously be arranged on the transverse carriage, which ensures a broad application spectrum for the grinding device.
The operation of the tools is particularly preferably carried out with geometry control since this permits a higher level of accuracy to be achieved.
According to one particularly advantageous aspect of the invention, the grinding device has measuring devices by means of which a position of the grinding device relative to the roller which is to be treated can be determined.
The measuring devices can preferably have at least two sensing devices for a reference object, which measuring devices can be embodied in the form of scanners, in particular laser scanners. Scanners of this type permit easy but very reliable sensing of the position of objects.
The reference object can particularly preferably be embodied in the form of a stretched wire, which wire is arranged essentially parallel to the roller axis of the roller which is to be treated and has a fixed, invariable geometric relationship with the roller axis.
This referencing permits the spatial position of the essential components of the device to be located precisely with respect to one another, with the result that possible inaccuracies in the mechanical foundations can be compensated.
The wire is preferably arranged in such a way that it can be sensed by the scanners, which is made possible by a corresponding geometry of the scanners.
The scanners can each preferably be arranged in pairs here both on the longitudinal carriage and on the transverse carriage. The selection can be carried out in each case here according to aspects such as the protection of the scanners during transportation, simple accessibility for the operating personnel etc.
Furthermore, the measuring devices can advantageously comprise at least one inclination sensor which is arranged on the transverse carriage and by which an inclination of the transverse carriage relative to the substructure can be sensed.
Likewise it is advantageous if the measuring devices have at least one measuring probe which is arranged on the transverse carriage and by which the roller surface which is to be treated can be sensed and/or the distance between the grinding device and the roller axis can be measured. The measuring probe can be embodied as an inductive measuring probe or as a laser probe.
One embodiment is particularly preferred in which at least one further measuring probe is provided which is arranged opposite the first measuring probe with respect to the roller axis, on a rear side of the roller, by means of which further measuring probe untrue running errors at the support points of the roller can be sensed.
The measured values of the scanners, of the inclination sensor, of the at least one measuring probe of the measuring devices can preferably be fed in for the purpose of performing open-loop and closed-loop control of the position of the tool (17) by means of actuating devices (21, 25, 26). The actuating devices may be embodied here, for example, in the form of piezo-actuators.
The tool can advantageously be pivoted in a plurality of planes with respect to the roller axis by means of at least one actuating device.
In addition, the tool can be adjustable in the direction of the roller axis by means of at least one actuating device. In this way, any desired position can be adopted and any desired presettable surface shape, such as, for example, in particular embossing, can be fabricated.
The invention will be described in more detail below with reference to the drawings on the basis of preferred exemplary embodiments. In the figures:
Figure 1 is a highly simplified basic outline of the grinding device configured according to the invention, in a plan view from above, Figures 2A-B show highly schematic illustrations of two possible measures for decoupling oscillations of the grinding device which is embodied according to the invention, Figure 3 shows a schematic lateral view of the grinding device according to the invention with two roller diameters or tool diameters, Figures 4A-C show highly schematic lateral illustrations of three possible foundations for a grinding device according to the invention, Figure 5 shows an exemplary embodiment of a bearing arrangement of the grinding device embodied according to the invention, Figure 6 shows two highly schematic perspective illustrations of the longitudinal carriage and of the transverse carriage of the grinding device according to the invention, Figures 7A-B show a lateral illustration and a plan view of a first preferred exemplary embodiment of a grinding device configured according to the invention, and Figures 8A-B show a lateral illustration and a plan view of a second preferred exemplary embodiment of a grinding device configured according to the invention.
Figure 1 is a highly schematic basic outline of a grinding device 1 according to the invention in a plan view from above.
The grinding device 1 is a mobile design here in its essential components and can be set up and dismantled within a short time as well as being transported at low cost and is therefore suitable in particular for use in paper factories which have paper machines with such long and heavy rollers that it is not economical to transport them to a service centre for grinding and/or not possible owing to legal requirements. These rollers 2 can be treated in situ at a location, such as for example a factory hall, suitable for this purpose, by means of the grinding device 1 according to the invention. After the grinding process, the grinding device 1 can be dismantled and transported to another paper factory, with the result that the expensive and costly installation of a fixed grinding device can be dispensed with. All that is necessary is to provide a foundation in the respective paper factory in order to be able to permit the renewed setting up of the grinding device 1 at the next grinding cycle.
The roller 2 which is to be ground is set up at the selected location on bearing blocks 3 with suitable foundations (not visible in figure 1). The mobile grinding device 1, which is equally suitable for grinding and measuring the roller surface which is to be treated is set up on guide rails 5 and moved axially on the latter along the roller 2, while the measuring devices which are described in more detail below replace an otherwise necessary grinding bed which has already been mentioned above.
In order to be able to achieve the necessary stiffness during the grinding process when the grinding device 1 according to the invention is used and in order to be able to compensate disruptive environmental influences in the form of the excitation of vibrations, there is therefore a need for a connection between the bearing blocks 3 of the roller 2 and the guide rails 5 for the grinding device 1 which is as rigid as possible.
Furthermore, despite the omission of a conventional grinding bed, a basic geometric relationship must be created and maintained between the grinding device 1 and the roller 2.
In order to damp vibrations, various concepts are possible, and therefore, for example, a passive isolating means can be used which is illustrated in a highly schematic form in figure 2A in that a frame 4 which is as rigid as possible is inserted into the substructure 6 which bears the bearing blocks 3 for the roller 2 and the guide rails 5 for the grinding device 1 and is additionally isolated from the substructure by a damping layer 7.
However, as an alternative to this, it is also possible to use actively compensating installation elements 8. A
frame 4, which is, however, rigidly connected to the substructure 6 in order to achieve a greater degree of basic rigidity, is also provided here. For the purpose of compensating travel excitations from the substructure 6, the grinding device 1 then has its own active compensation elements 8 or actuators, as is apparent from figure 2B.
The bearing blocks 3 of the roller 2 must ensure a position of the roller axis in the vertical and horizontal directions which can be used as a reference.
Depending on the size of the roller 2 which is to be treated and/or in the case of fluctuating dimensions thereof, the bearing blocks 3 can advantageously be adjusted in at least one direction. The position of the bearing blocks 3 can be adjusted by virtue of the possibility of sliding the bearing blocks 3 relative to one another in the axial direction and/or relative to the substructure 6 for rollers 2 of different lengths, wherein a rail system (not shown in more detail in the figures) which is parallel to the guide rails 5 of the grinding device 1 can be used. Furthermore, a continuously adjustable bearing point 9 of the roller 2 can be provided in the bearing block 3 for different roller diameters, or at least two discrete bearing points 9a, 9b have to be provided for two groups of roller diameters. In both cases, the roller axis can be slid parallel to the substructure 6 in the horizontal direction, as is illustrated schematically in a lateral view in figure 3. An embodiment with two discrete bearing points 9a, 9b is a simpler solution, while an infinitely variable adjustment of the bearing point 9 opens up a wider range of fields of use.
Furthermore, it is necessary to ensure that the axes of the roller 2 and of a tool 17 which treat the roller surface are at the same height. This can be made possible by virtue of an adjustment possibility of the tool height and by virtue of an adjustment possibility of the bearing points 9a, 9b of the roller 2 in the bearing blocks 3 in the vertical direction. A roller drive (not illustrated in more detail in the figures) and the structural integration thereof can be arranged in a known fashion as in conventional grinding machines.
As a result of the fact that the guide rails 5 require a high degree of accuracy during their laying in order to ensure the accuracy, required for the grinding process, in the treatment of the roller surface, it is recommended to attach the guide rails 5 permanently to the substructure 6. Various possibilities, as are respectively illustrated in lateral highly schematic views in figures 4A to 4C, are conceivable for connection between the guide rails 5 and the substructure 6.
It is basically possible to screw the guide rails 5 directly to the substructure 6, as is illustrated schematically in figure 4A. This variant has the smallest degree of expenditure for the pre-processing of the machine location, but does not result in the desired accuracy during the treatment as a result of the low level of accuracy which is achieved in the orientation of the guide rails 5. A further embodiment variant can provide for the guide rails 5 to be screwed onto in each case one carrier 10 which is let into the substructure 6. This embodiment can be seen in figure 4B. The carrier 10 can be treated here in such a way that the connecting structure for a guide rail 5 satisfies the requirements. However, the position of the guide rails 5 with respect to one another would not be sufficiently precisely defined here either. The third and preferred embodiment which is illustrated in figure 4C can be derived as a consequence of the latter and on the basis of the general considerations about the substructure 6 which are described above. The carriers 10 are connected to one another here by the frame 4 which has already been mentioned above, as a result of which the geometric position of the guide rails 5 with respect to one another is defined.
The frame 4 which is let into the substructure 6 therefore serves for the guide rails 5 as a type of simple machine bed, it defines the geometric position of the guide rails 5 and can also serve to increase the rigidity in accordance with its configuration.
Bearings 11 which communicate with the guide rails 5 on a longitudinal carriage 15, described in more detail below, of the grinding device 1 serve as an interface between the mobile and the stationary components of the grinding device 1. Possible embodiment variants for the bearings 11 are both sliding guides and rolling guides, wherein the latter constitute the preferred embodiment both from a technical and economic point of view since they are defined by a high degree of rigidity and accuracy as well as a low degree of operational expenditure.
Two different embodiments can likewise be considered for the guide rails 5. On the one hand, an open guide system, also known as a fixed/freely moving bearing system, as illustrated in a schematic lateral view in figure 5, can be conceived by using recirculating roller shoes 12. In this context, one of the guide rails 5 interacts with a fixed bearing 12a, and the other with a freely moving bearing 12b. The guide rail 5a which interacts with the fixed bearing 12a has here a trapezoidal cross section which tapers in the direction of the grinding device 1 and on whose lateral faces 13 two bearing rollers 12a engage, while the freely moving bearing 12b merely rests on the second guide rail 5b.
The advantage of such an open guide system is the possibility of being able to easily fit on the mobile grinding device 1 to the guide rails 5 without expenditure on mounting. Furthermore, the sensitivity with respect to geometric faults in the transverse direction with respect to the movement direction is low as a result of the freely moving side. The illustrated open guide is also conceivable with respect to the lifting-off forces which do not occur or which occur only to a small degree, and it is not absolutely necessary for engagement on multiple sides.
On the other hand, the use of bearings 11 which lead to a closed system and engagement on multiple sides is however also conceivable and possible. As a result, support against relatively strong lifting-off forces is also possible. With respect to the suitability as an interface between stationary and mobile components of the grinding device 1, this embodiment has, however, the disadvantage that the closed bearings 11 cannot be lifted off. They could, for example, be fitted permanently on the guide rails 5 by mounting on a base plate. For this purpose, the bearings 11 and base plate have to be provided separately at each location of use.
This is, at least a cost factor, but in addition stringent requirements are made of the parallelism of = CA 02761841 2011-11-14 the guide rails 5 due to the overdeterminedness of the system, and this results in increased requirements of the frame structure 4.
The lack of a conventional machine bed for receiving all the components of the grinding device 1 inevitably also results in a lower degree of geometric accuracy of the guide rails 5. This can be compensated by using a corresponding direct measuring method. In addition to the errors in the horizontal direction which occur directly, deviations in the vertical position between the roller 2 which is to be treated and a tool 17 also lead to differences in the engagement depth and therefore to treatment errors. Depending on the foundations of the grinding device 1 and therefore on the achievable geometric accuracy of the guide rails 5, relative movements occur between the tool 17 and the roller 2 in the horizontal direction. The vertical errors also have to be compensated as soon as they have a relevant influence on the working accuracy. The sensitivity with respect to errors in the vertical direction increases as the axle spacing between the roller 2 and the tool 17 becomes smaller.
A suitable stationary reference object 14, whose position relative to a global coordinate system K
defined by the roller axis is known and is invariable, serves as a reference for the measurement of the roller 2 before the treatment. In the illustrated exemplary embodiment, the reference object 14 is embodied in the form of a stretched wire 14, but other reference objects 14, such as for example a measuring rail in a defined position, are also possible. The position of the wire 14 is determined by calibration using at least suitable measuring devices, as explained below in more detail.
The wire 14 serves as a reference for the roller axis.
Consequently, its position with respect to the roller 2 or the roller axis must be invariable. The wire 14 is held in the exemplary embodiment on both sides by vertically and/or radially adjustable rollers, and on one side it is rigidly attached and on the other stretched by a weight with a known mass. This arrangement is in principle known and is used according to the prior art in the grinding method described above. The mounts of the wire 14 have to be rigidly connected to the bearing blocks 3 of the roller 2 or to the foundation 4. However, it is also conceivable to assign the mounts to the mobile components of the grinding device 1.
The longitudinal carriage 15, already mentioned further above, of the grinding device 1 is the carrier of the measuring devices 16 and of the tools 17 which are described below. Both the measuring devices 16 and the tools 17 are preferably arranged here on a transverse carriage 18 which for its part is arranged on the longitudinal carriage 15. As is apparent from figure 6 in a highly schematic form in two perspective views, a rail bearing system 19 is also provided as a coupling point between the longitudinal carriage 15 and the transverse carriage 18. The longitudinal carriage 15 moves along an extension direction of the roller axis, that is to say longitudinally with respect to the roller 2, while the transverse carriage 18 can be moved toward the roller 2 in the radial direction. The movement direction of the longitudinal carriage 15 is therefore oriented essentially at a right angle to that of the transverse carriage 18.
In order to be able to manufacture specific embossing or surface shapes during the treatment of the roller, the transverse carriage 18 is additionally also mounted in a pivotable fashion with respect to the longitudinal carriage 15. A pivotable bearing arrangement of the tool 17 with respect to the transverse carriage 18 is also possible in order to achieve this objective.
The rollers which are used in the paper industry are subject to unavoidable wear. The re-processing is at present usually carried out by transporting the rollers to a service centre and conditioning them there.
However, since the dimensions and the weight of these rollers are continuously increasing - over 100 t weight and 12 m length are no longer unusual - an alternative concept is both economically desirable and necessary, for example due to restrictions on goods traffic. A
grinding device which is mobile and can be easily transported to a paper factory and operated there is suitable for this.
A device and a method for grinding roller surfaces which are described in WO 01/49451 Al are already known for dry cylinders of paper machines for producing tissue paper. The dry cylinders in this type of paper machine are, on the one hand, very large and, on the other hand, are difficult to disinstall due to their heatable configuration, for which reason the surface of the so-called yankee cylinders always have to be treated in situ. WO 01/49451 Al describes a grinding device for grinding such a yankee cylinder, wherein the grinding device which can be moved in a direction which is essentially parallel to the roller and can be displaced toward and away from the roller. Furthermore, a measuring system which is assigned to the grinding device and can be moved therewith is provided for measuring the roller, relative to at least one reference line which is provided outside the roller and is adjusted parallel to the axis of the roller, wherein the relative position is determined in a plane which is preferably perpendicular to the reference line. The grinding process which is carried out by the grinding device, i.e. the contact pressure force or the contact pressure, is regulated on the basis of the measured values which are obtained by the measuring system. The grinding process therefore takes place with force control on the basis of a previous measurement of the surface.
A disadvantage with this known grinding device is here, on the one hand, that the measuring system does not reach the level of accuracy which is required for treating roller surfaces with various coverings, and the force-controlled grinding is difficult with soft or elastic coverings. The yankee cylinders which are mentioned further above are made of metal or are provided with a ceramic coating or hard metal coating, but are not covered with a soft covering.
In addition the suitability of the belt grinding technology, used according to WO 01/49451 Al, for treating soft roller coverings is not provided to the desired degree.
Furthermore, the guide which is used in the device known from WO 01/49451 Al, on the scraper bar, is not available, and said device would also not be suitable for grinding with geometric guidance.
Conventional grinding machines, such as are known, for example, from EP 1 584 396 A, have the disadvantage of being entirely secured to one location. This is due, in particular to the formation of the grinding beds for these grinding machines. Such grinding beds usually comprise in this context a concrete square of large dimensions and mass, which is arranged in a suitable recess in the substructure, for example of a hall, and is mounted on springs for decoupling oscillation. Such a grinding bed can weigh several hundred tonnes and therefore can be manufactured only at extreme cost. In addition, such a grinding bed runs contrary to any requirement for mobility. Grinding machines with such a grinding bed are built exclusively for stationary use and cannot be transported.
Accordingly, the object of the invention is to specify a grinding device for rollers which is mobile, does not require a costly and heavy grinding machine bed and is suitable for use with any desired roller surfaces.
In this context, important criteria are the requirements for accuracy and the unsusceptibility to faults as well as the coverage of a wide application field.
According to the invention, there is the provision that the grinding device comprises stationary components and mobile components which can be separated from one another, and wherein the stationary components comprise guide rails which extend essentially parallel to a roller axis of the roller which is to be treated and are connected to a substructure.
The stationary components move here within a framework which is distinguished, in comparison with normal grinding beds, by ease of installation, small requirement for foundations and cost-effectiveness. The stationary components can therefore be present in any paper factory which desires them, while the mobile components can be easily distanced from the stationary components, and the mobile components can then be moved to other locations in order to be used there.
Paper factories are therefore neither forced to set up a separate, very costly stationary grinding device, nor must heavy and long rollers be sent to a service centre at enormous cost. The acquisition of the mobile components is also dispensed with since they can be ordered, used and transported away again as required in the form of a service performance. The cost factor for fixed installations is therefore low.
Further advantageous aspects and refinement variants can be found in the dependent claims.
The guide rails can be advantageously connected directly to the substructure with carriers which are inserted into the substructure or with a frame which is inserted into the substructure, with the result that a foundation arrangement which corresponds to the required accuracy levels can be achieved.
The roller which is to be ground can preferably be arranged on bearing blocks which are connected to the substructure.
In order to decouple the bearing blocks and/or the guide rails, passive insulation against excitation of vibrations in the form of a damping layer and/or damping elements in the form of spring elements can be provided between the substructure and the bearing blocks and/or between the substructure and the guide rails.
The bearing blocks and/or the guide rails can also particularly preferably have devices in the form of actuators which can be open-loop and closed-loop controlled, for actively bringing about decoupling from the substructure. This is a costly but very reliable form of damping. Mixed forms composed of active and passive damping are also possible.
In order to permit both large and small roller diameters to be treated and to be able to set the position of the tool for surface treatment correctly with respect to the roller axis, it is advantageous if the bearing points of the roller in the bearing blocks are both horizontally and vertically adjustable.
Mobile components of the grinding device can advantageously comprise a longitudinal carriage which is movably guided on the guide rails and is arranged in such a way that it can be moved or slid along an extension direction of the roller axis of the roller which is to be treated.
The longitudinal carriage can preferably have bearings which interact with the guide rails. Preferred forms of bearing are in this context sliding bearings or roller bearings. A particularly preferred embodiment provides here for the formation of a fixed/freely moving bearing with the circulating roller shoes which have a high degree of accuracy and good guidance with little susceptibility to offsets in the transverse direction with respect to the direction of movement.
Preferably a transverse carriage is arranged so as to be movable or slidable on the longitudinal carriage, wherein a movement direction of the transverse carriage is oriented essentially perpendicularly to the movement direction of the longitudinal carriage. As a result, the desired means of freedom in the movement relative to the roller can be actuated directly and in a simple way.
In order to be able to carry out specific embossing or form other surface structures in the roller surface, it is also advantageous if the transverse carriage can be horizontally and/or vertically pivoted with respect to the longitudinal carriage.
A rail bearing system can also be formed between the longitudinal carriage and the transverse carriage, which rail bearing system can be embodied in such a way that, in particular, bearings engage around guide rails since as a result it is possible to provide protection against lifting-off forces during the processing.
The transverse carriage can be arranged in such a way that it is secured on the longitudinal carriage or can be removed therefrom. A secured arrangement facilitates the expenditure on mounting since the transverse carriage does not have to be specially mounted, and on the other hand a removable transverse carriage contributes to the compactness of the device.
A tool, in particular a grinding disk, a belt grinder, a grooving device, a superfinishing device or a honing device can advantageously be arranged on the transverse carriage, which ensures a broad application spectrum for the grinding device.
The operation of the tools is particularly preferably carried out with geometry control since this permits a higher level of accuracy to be achieved.
According to one particularly advantageous aspect of the invention, the grinding device has measuring devices by means of which a position of the grinding device relative to the roller which is to be treated can be determined.
The measuring devices can preferably have at least two sensing devices for a reference object, which measuring devices can be embodied in the form of scanners, in particular laser scanners. Scanners of this type permit easy but very reliable sensing of the position of objects.
The reference object can particularly preferably be embodied in the form of a stretched wire, which wire is arranged essentially parallel to the roller axis of the roller which is to be treated and has a fixed, invariable geometric relationship with the roller axis.
This referencing permits the spatial position of the essential components of the device to be located precisely with respect to one another, with the result that possible inaccuracies in the mechanical foundations can be compensated.
The wire is preferably arranged in such a way that it can be sensed by the scanners, which is made possible by a corresponding geometry of the scanners.
The scanners can each preferably be arranged in pairs here both on the longitudinal carriage and on the transverse carriage. The selection can be carried out in each case here according to aspects such as the protection of the scanners during transportation, simple accessibility for the operating personnel etc.
Furthermore, the measuring devices can advantageously comprise at least one inclination sensor which is arranged on the transverse carriage and by which an inclination of the transverse carriage relative to the substructure can be sensed.
Likewise it is advantageous if the measuring devices have at least one measuring probe which is arranged on the transverse carriage and by which the roller surface which is to be treated can be sensed and/or the distance between the grinding device and the roller axis can be measured. The measuring probe can be embodied as an inductive measuring probe or as a laser probe.
One embodiment is particularly preferred in which at least one further measuring probe is provided which is arranged opposite the first measuring probe with respect to the roller axis, on a rear side of the roller, by means of which further measuring probe untrue running errors at the support points of the roller can be sensed.
The measured values of the scanners, of the inclination sensor, of the at least one measuring probe of the measuring devices can preferably be fed in for the purpose of performing open-loop and closed-loop control of the position of the tool (17) by means of actuating devices (21, 25, 26). The actuating devices may be embodied here, for example, in the form of piezo-actuators.
The tool can advantageously be pivoted in a plurality of planes with respect to the roller axis by means of at least one actuating device.
In addition, the tool can be adjustable in the direction of the roller axis by means of at least one actuating device. In this way, any desired position can be adopted and any desired presettable surface shape, such as, for example, in particular embossing, can be fabricated.
The invention will be described in more detail below with reference to the drawings on the basis of preferred exemplary embodiments. In the figures:
Figure 1 is a highly simplified basic outline of the grinding device configured according to the invention, in a plan view from above, Figures 2A-B show highly schematic illustrations of two possible measures for decoupling oscillations of the grinding device which is embodied according to the invention, Figure 3 shows a schematic lateral view of the grinding device according to the invention with two roller diameters or tool diameters, Figures 4A-C show highly schematic lateral illustrations of three possible foundations for a grinding device according to the invention, Figure 5 shows an exemplary embodiment of a bearing arrangement of the grinding device embodied according to the invention, Figure 6 shows two highly schematic perspective illustrations of the longitudinal carriage and of the transverse carriage of the grinding device according to the invention, Figures 7A-B show a lateral illustration and a plan view of a first preferred exemplary embodiment of a grinding device configured according to the invention, and Figures 8A-B show a lateral illustration and a plan view of a second preferred exemplary embodiment of a grinding device configured according to the invention.
Figure 1 is a highly schematic basic outline of a grinding device 1 according to the invention in a plan view from above.
The grinding device 1 is a mobile design here in its essential components and can be set up and dismantled within a short time as well as being transported at low cost and is therefore suitable in particular for use in paper factories which have paper machines with such long and heavy rollers that it is not economical to transport them to a service centre for grinding and/or not possible owing to legal requirements. These rollers 2 can be treated in situ at a location, such as for example a factory hall, suitable for this purpose, by means of the grinding device 1 according to the invention. After the grinding process, the grinding device 1 can be dismantled and transported to another paper factory, with the result that the expensive and costly installation of a fixed grinding device can be dispensed with. All that is necessary is to provide a foundation in the respective paper factory in order to be able to permit the renewed setting up of the grinding device 1 at the next grinding cycle.
The roller 2 which is to be ground is set up at the selected location on bearing blocks 3 with suitable foundations (not visible in figure 1). The mobile grinding device 1, which is equally suitable for grinding and measuring the roller surface which is to be treated is set up on guide rails 5 and moved axially on the latter along the roller 2, while the measuring devices which are described in more detail below replace an otherwise necessary grinding bed which has already been mentioned above.
In order to be able to achieve the necessary stiffness during the grinding process when the grinding device 1 according to the invention is used and in order to be able to compensate disruptive environmental influences in the form of the excitation of vibrations, there is therefore a need for a connection between the bearing blocks 3 of the roller 2 and the guide rails 5 for the grinding device 1 which is as rigid as possible.
Furthermore, despite the omission of a conventional grinding bed, a basic geometric relationship must be created and maintained between the grinding device 1 and the roller 2.
In order to damp vibrations, various concepts are possible, and therefore, for example, a passive isolating means can be used which is illustrated in a highly schematic form in figure 2A in that a frame 4 which is as rigid as possible is inserted into the substructure 6 which bears the bearing blocks 3 for the roller 2 and the guide rails 5 for the grinding device 1 and is additionally isolated from the substructure by a damping layer 7.
However, as an alternative to this, it is also possible to use actively compensating installation elements 8. A
frame 4, which is, however, rigidly connected to the substructure 6 in order to achieve a greater degree of basic rigidity, is also provided here. For the purpose of compensating travel excitations from the substructure 6, the grinding device 1 then has its own active compensation elements 8 or actuators, as is apparent from figure 2B.
The bearing blocks 3 of the roller 2 must ensure a position of the roller axis in the vertical and horizontal directions which can be used as a reference.
Depending on the size of the roller 2 which is to be treated and/or in the case of fluctuating dimensions thereof, the bearing blocks 3 can advantageously be adjusted in at least one direction. The position of the bearing blocks 3 can be adjusted by virtue of the possibility of sliding the bearing blocks 3 relative to one another in the axial direction and/or relative to the substructure 6 for rollers 2 of different lengths, wherein a rail system (not shown in more detail in the figures) which is parallel to the guide rails 5 of the grinding device 1 can be used. Furthermore, a continuously adjustable bearing point 9 of the roller 2 can be provided in the bearing block 3 for different roller diameters, or at least two discrete bearing points 9a, 9b have to be provided for two groups of roller diameters. In both cases, the roller axis can be slid parallel to the substructure 6 in the horizontal direction, as is illustrated schematically in a lateral view in figure 3. An embodiment with two discrete bearing points 9a, 9b is a simpler solution, while an infinitely variable adjustment of the bearing point 9 opens up a wider range of fields of use.
Furthermore, it is necessary to ensure that the axes of the roller 2 and of a tool 17 which treat the roller surface are at the same height. This can be made possible by virtue of an adjustment possibility of the tool height and by virtue of an adjustment possibility of the bearing points 9a, 9b of the roller 2 in the bearing blocks 3 in the vertical direction. A roller drive (not illustrated in more detail in the figures) and the structural integration thereof can be arranged in a known fashion as in conventional grinding machines.
As a result of the fact that the guide rails 5 require a high degree of accuracy during their laying in order to ensure the accuracy, required for the grinding process, in the treatment of the roller surface, it is recommended to attach the guide rails 5 permanently to the substructure 6. Various possibilities, as are respectively illustrated in lateral highly schematic views in figures 4A to 4C, are conceivable for connection between the guide rails 5 and the substructure 6.
It is basically possible to screw the guide rails 5 directly to the substructure 6, as is illustrated schematically in figure 4A. This variant has the smallest degree of expenditure for the pre-processing of the machine location, but does not result in the desired accuracy during the treatment as a result of the low level of accuracy which is achieved in the orientation of the guide rails 5. A further embodiment variant can provide for the guide rails 5 to be screwed onto in each case one carrier 10 which is let into the substructure 6. This embodiment can be seen in figure 4B. The carrier 10 can be treated here in such a way that the connecting structure for a guide rail 5 satisfies the requirements. However, the position of the guide rails 5 with respect to one another would not be sufficiently precisely defined here either. The third and preferred embodiment which is illustrated in figure 4C can be derived as a consequence of the latter and on the basis of the general considerations about the substructure 6 which are described above. The carriers 10 are connected to one another here by the frame 4 which has already been mentioned above, as a result of which the geometric position of the guide rails 5 with respect to one another is defined.
The frame 4 which is let into the substructure 6 therefore serves for the guide rails 5 as a type of simple machine bed, it defines the geometric position of the guide rails 5 and can also serve to increase the rigidity in accordance with its configuration.
Bearings 11 which communicate with the guide rails 5 on a longitudinal carriage 15, described in more detail below, of the grinding device 1 serve as an interface between the mobile and the stationary components of the grinding device 1. Possible embodiment variants for the bearings 11 are both sliding guides and rolling guides, wherein the latter constitute the preferred embodiment both from a technical and economic point of view since they are defined by a high degree of rigidity and accuracy as well as a low degree of operational expenditure.
Two different embodiments can likewise be considered for the guide rails 5. On the one hand, an open guide system, also known as a fixed/freely moving bearing system, as illustrated in a schematic lateral view in figure 5, can be conceived by using recirculating roller shoes 12. In this context, one of the guide rails 5 interacts with a fixed bearing 12a, and the other with a freely moving bearing 12b. The guide rail 5a which interacts with the fixed bearing 12a has here a trapezoidal cross section which tapers in the direction of the grinding device 1 and on whose lateral faces 13 two bearing rollers 12a engage, while the freely moving bearing 12b merely rests on the second guide rail 5b.
The advantage of such an open guide system is the possibility of being able to easily fit on the mobile grinding device 1 to the guide rails 5 without expenditure on mounting. Furthermore, the sensitivity with respect to geometric faults in the transverse direction with respect to the movement direction is low as a result of the freely moving side. The illustrated open guide is also conceivable with respect to the lifting-off forces which do not occur or which occur only to a small degree, and it is not absolutely necessary for engagement on multiple sides.
On the other hand, the use of bearings 11 which lead to a closed system and engagement on multiple sides is however also conceivable and possible. As a result, support against relatively strong lifting-off forces is also possible. With respect to the suitability as an interface between stationary and mobile components of the grinding device 1, this embodiment has, however, the disadvantage that the closed bearings 11 cannot be lifted off. They could, for example, be fitted permanently on the guide rails 5 by mounting on a base plate. For this purpose, the bearings 11 and base plate have to be provided separately at each location of use.
This is, at least a cost factor, but in addition stringent requirements are made of the parallelism of = CA 02761841 2011-11-14 the guide rails 5 due to the overdeterminedness of the system, and this results in increased requirements of the frame structure 4.
The lack of a conventional machine bed for receiving all the components of the grinding device 1 inevitably also results in a lower degree of geometric accuracy of the guide rails 5. This can be compensated by using a corresponding direct measuring method. In addition to the errors in the horizontal direction which occur directly, deviations in the vertical position between the roller 2 which is to be treated and a tool 17 also lead to differences in the engagement depth and therefore to treatment errors. Depending on the foundations of the grinding device 1 and therefore on the achievable geometric accuracy of the guide rails 5, relative movements occur between the tool 17 and the roller 2 in the horizontal direction. The vertical errors also have to be compensated as soon as they have a relevant influence on the working accuracy. The sensitivity with respect to errors in the vertical direction increases as the axle spacing between the roller 2 and the tool 17 becomes smaller.
A suitable stationary reference object 14, whose position relative to a global coordinate system K
defined by the roller axis is known and is invariable, serves as a reference for the measurement of the roller 2 before the treatment. In the illustrated exemplary embodiment, the reference object 14 is embodied in the form of a stretched wire 14, but other reference objects 14, such as for example a measuring rail in a defined position, are also possible. The position of the wire 14 is determined by calibration using at least suitable measuring devices, as explained below in more detail.
The wire 14 serves as a reference for the roller axis.
Consequently, its position with respect to the roller 2 or the roller axis must be invariable. The wire 14 is held in the exemplary embodiment on both sides by vertically and/or radially adjustable rollers, and on one side it is rigidly attached and on the other stretched by a weight with a known mass. This arrangement is in principle known and is used according to the prior art in the grinding method described above. The mounts of the wire 14 have to be rigidly connected to the bearing blocks 3 of the roller 2 or to the foundation 4. However, it is also conceivable to assign the mounts to the mobile components of the grinding device 1.
The longitudinal carriage 15, already mentioned further above, of the grinding device 1 is the carrier of the measuring devices 16 and of the tools 17 which are described below. Both the measuring devices 16 and the tools 17 are preferably arranged here on a transverse carriage 18 which for its part is arranged on the longitudinal carriage 15. As is apparent from figure 6 in a highly schematic form in two perspective views, a rail bearing system 19 is also provided as a coupling point between the longitudinal carriage 15 and the transverse carriage 18. The longitudinal carriage 15 moves along an extension direction of the roller axis, that is to say longitudinally with respect to the roller 2, while the transverse carriage 18 can be moved toward the roller 2 in the radial direction. The movement direction of the longitudinal carriage 15 is therefore oriented essentially at a right angle to that of the transverse carriage 18.
In order to be able to manufacture specific embossing or surface shapes during the treatment of the roller, the transverse carriage 18 is additionally also mounted in a pivotable fashion with respect to the longitudinal carriage 15. A pivotable bearing arrangement of the tool 17 with respect to the transverse carriage 18 is also possible in order to achieve this objective.
Technical grinding limits are placed on the pivotings to ensure, for example, that the grinding disk does not engage with its edge on the roller 2 and therefore a pivoting range of approximately 10 is sufficient.
A guide which permits bearings to engage around guide rails is advantageous for the transverse carriage 18 (not illustrated in more detail in the figure for reasons of clarity), since the transverse carriage 18 has to be protected against lifting-off forces because of its comparatively low weight. The transverse carriage 18 can be fitted permanently on the longitudinal carriage 15 here or be capable of being removed for transportation.
In the exemplary embodiment illustrated in the figures, for example a grinding disk is illustrated as a tool 17. In this context, the grinding means which are used at present, for example grinding stones of 300-900 mm in diameter can be used. The latter have the advantage of known sufficient technological properties. The large span width of the diameters requires, however, a large adjustment range of the transverse carriage 18.
Furthermore, ceramically bound disks (CBN or diamond) can be used. These only have small wear ranges (5 mm) and a significantly smaller range would therefore be sufficient for advancing.
Furthermore, the transverse carriage 18 can also be prepared to receive devices for performing superfinishing or honing (not illustrated in more detail in the exemplary embodiment) . A drive for the respective tool 17 can be provided on the longitudinal carriage 15, the transverse carriage 18 or else externally.
In order to improve the mechanical properties, in particular in order to increase the stability and to reduce the possibility of vibrations being excited, the longitudinal carriage 15 must be embodied with as high a mass as possible. This can be done, for example, by means of free volumes of cast mineral, filling with sand or water, insertion of weight-increasing plates or the like.
Figure 7A to 7B and 8A to 8B illustrate two exemplary embodiments of a grinding device 1, embodied according to the invention, in a highly schematic form, in a lateral view and in a plan view, respectively. In this context, it is to be noted in particular that the external shape and the closed box formation are not limited to the illustrated exemplary embodiments which have essentially a right-parallelepiped-shaped basic form but this is merely a simplification which permits a clear illustration of the features which are essential to the invention. It is possible to select other shapes, which, for example, increase the operational reliability for the operating personnel by means of rounded-off edges, as well as other structures such as, for example, grille structures if, as a result, the handling, the arrangement of the tools 17 which are mounted on the longitudinal carriage 15 or the introduction of weight-increasing plates for example are made easier.
However, the grinding devices 1 which are illustrated by way of example and which represent the order of magnitude of the respective components, since, for example, the freedom of collision of the longitudinal carriage 15 with the roller surface has to be ensured for all the workpiece diameters and the freedom of collision of the tools 17 with the longitudinal carriage 15 has to be ensured. Here, corresponding pockets or recesses 20 can be provided (see for example figure 8A) in order nevertheless to implement a compact design and therefore ensure a good level of rigidity of the device with a suitably positioned centre of gravity.
A guide which permits bearings to engage around guide rails is advantageous for the transverse carriage 18 (not illustrated in more detail in the figure for reasons of clarity), since the transverse carriage 18 has to be protected against lifting-off forces because of its comparatively low weight. The transverse carriage 18 can be fitted permanently on the longitudinal carriage 15 here or be capable of being removed for transportation.
In the exemplary embodiment illustrated in the figures, for example a grinding disk is illustrated as a tool 17. In this context, the grinding means which are used at present, for example grinding stones of 300-900 mm in diameter can be used. The latter have the advantage of known sufficient technological properties. The large span width of the diameters requires, however, a large adjustment range of the transverse carriage 18.
Furthermore, ceramically bound disks (CBN or diamond) can be used. These only have small wear ranges (5 mm) and a significantly smaller range would therefore be sufficient for advancing.
Furthermore, the transverse carriage 18 can also be prepared to receive devices for performing superfinishing or honing (not illustrated in more detail in the exemplary embodiment) . A drive for the respective tool 17 can be provided on the longitudinal carriage 15, the transverse carriage 18 or else externally.
In order to improve the mechanical properties, in particular in order to increase the stability and to reduce the possibility of vibrations being excited, the longitudinal carriage 15 must be embodied with as high a mass as possible. This can be done, for example, by means of free volumes of cast mineral, filling with sand or water, insertion of weight-increasing plates or the like.
Figure 7A to 7B and 8A to 8B illustrate two exemplary embodiments of a grinding device 1, embodied according to the invention, in a highly schematic form, in a lateral view and in a plan view, respectively. In this context, it is to be noted in particular that the external shape and the closed box formation are not limited to the illustrated exemplary embodiments which have essentially a right-parallelepiped-shaped basic form but this is merely a simplification which permits a clear illustration of the features which are essential to the invention. It is possible to select other shapes, which, for example, increase the operational reliability for the operating personnel by means of rounded-off edges, as well as other structures such as, for example, grille structures if, as a result, the handling, the arrangement of the tools 17 which are mounted on the longitudinal carriage 15 or the introduction of weight-increasing plates for example are made easier.
However, the grinding devices 1 which are illustrated by way of example and which represent the order of magnitude of the respective components, since, for example, the freedom of collision of the longitudinal carriage 15 with the roller surface has to be ensured for all the workpiece diameters and the freedom of collision of the tools 17 with the longitudinal carriage 15 has to be ensured. Here, corresponding pockets or recesses 20 can be provided (see for example figure 8A) in order nevertheless to implement a compact design and therefore ensure a good level of rigidity of the device with a suitably positioned centre of gravity.
The drive of the grinding device 1, which drive is not illustrated in the figures for the sake of clarity, can, with suitable adaptation of the components, make use of various possible drive concepts. Owing to the long displacement travel, a toothed rack/pinion drive is an advantageous embodiment variant for the longitudinal advancing along the roller 2 which is to be treated. However, other drive concepts such as ball screw drives or linear direct drives are also possible.
Such drives and their arrangement on the object which is to be driven are known in principle, and a description will therefore not be given at this point.
Likewise desired drive concepts which are known in principle and which provide the required accuracy and resolution of movement in the advancing movement can be applied to drive the transverse carriage 18.
Regulated movement axes are required for the positioning of the transverse carriage 18 and for the adjustment during operation, said movement axes implementing axial movement (advancing in the z direction) and radial forward movement in the x direction including compensation of guide path deviations as well as for a movement axis, necessary for calibration, for the pivoting of the measuring devices 16.
The transverse carriage 18 is, as is, for example, clearly visible in figure 7A, embodied in the form of a correspondingly stiff frame structure. The drive of the tool 17 can be implemented directly by a motor spindle or indirectly by a transmission means using a belt. For the fine adjustment of the tool 17 it is possible to provide additional movement axes, for example in the form of piezo-actuators 21 or other precisely adjustable actuators for actively aligning the grinding axis (see below).
Such drives and their arrangement on the object which is to be driven are known in principle, and a description will therefore not be given at this point.
Likewise desired drive concepts which are known in principle and which provide the required accuracy and resolution of movement in the advancing movement can be applied to drive the transverse carriage 18.
Regulated movement axes are required for the positioning of the transverse carriage 18 and for the adjustment during operation, said movement axes implementing axial movement (advancing in the z direction) and radial forward movement in the x direction including compensation of guide path deviations as well as for a movement axis, necessary for calibration, for the pivoting of the measuring devices 16.
The transverse carriage 18 is, as is, for example, clearly visible in figure 7A, embodied in the form of a correspondingly stiff frame structure. The drive of the tool 17 can be implemented directly by a motor spindle or indirectly by a transmission means using a belt. For the fine adjustment of the tool 17 it is possible to provide additional movement axes, for example in the form of piezo-actuators 21 or other precisely adjustable actuators for actively aligning the grinding axis (see below).
The following terminology is used for the coordinate systems K and K' in figures 7A, 7B, 8A and 8B: in the global coordinate system K the z direction extends along the roller axis, the x direction coincides with the radial forward movement axis of the tool 17 and the y direction specifies the vertical. Correspondingly, the same directions with u (corresponds to x), v (corresponds to y) and w (corresponds to z) in the local coordinate system K'. Furthermore, the designations xi, y1, zI for a sensing device 22 on the left in the plan view, and xr, yr, Zr for a sensing device 22 which is on the right in the plan view are present.
The two sensing devices 22 or scanners 22, for example laser scanners, in the exemplary embodiment detect the reference wire 14 and permit, in conjunction with an inclination sensor 23, the position and direction of a local coordinate system K' on the transverse carriage 18 to be determined. The scanners 22 can be embodied here, as illustrated in figure 7A, on the transverse carriage 18, or, as is apparent from figure 8A, can be arranged in the longitudinal carriage 15. The selection can take place as desired in accordance with, for example, criteria of ease of operation, of protected arrangement, etc.
For the sensing of the surface of the roller 2 by means of a measuring probe 24, it is necessary to be able to adjust the measuring probe 24 in order to maintain the measuring range depending on the current size of the tool 17 (in the exemplary embodiment of the grinding disk) . This can be implemented in discrete steps since no change is necessary during the measuring process.
The spatial position of the measuring devices 16 with respect to the local system (K') either has to be known or can be determined from the current position of the movement axes. It is absolutely necessary to measure the longitudinal carriage 15 of the grinding device 1 in this respect.
In the illustrated exemplary embodiment, the measuring devices 16 comprise, as described, two scanners 22 and an inclination sensor 23, which are arranged on the transverse carriage 18 of the grinding device 1. This makes it possible to determine the position and orientation of the local coordinate system K' on the longitudinal carriage 15 in which the position of the measuring devices 16 and of the tool 17 are known.
During the treatment of the roller 2, the setpoint values for the forward movement are adapted on the basis of the determined deviations between the global coordinate systems K and the local coordinate system K'.
Conventionally already known measuring probes 24 are possible for the surface treatment. Inductive measuring probes 24, which have a high degree of accuracy (approximately 0.1 pm) and are suitable for all surfaces in question are usually already in use for this purpose. A disadvantage is their limited dynamics, for which reason under said circumstances the rotational speed of the roller has to be limited during measurement. Complete, uninterrupted measurement then takes a correspondingly long time. Alternatively, laser measurement systems can be applied which nowadays also permit mirrored surfaces to be measured. These operate in a contactless fashion and have now also achieved accuracy levels of approximately 0.2 pm. Mechanical systems for moving the measuring probe 24 can be dispensed with here because the measuring probe 24 does not have to be moved back during grinding, in contrast to an inductive measuring probe 24.
The measured value of the system with the results of the referencing and the fixed and known positions of the measuring devices 16 provide a measuring point on the roller surface expressed in a radius with respect to the roller axis. When the roller 2 is rotating, the measuring points can be set either during continuous axial movement of the longitudinal carriage 15 along the roller 2 longitudinally with respect to a helical line, or multiple rotations can be used to acquire measuring points during incremental movement. A
permanently available signal for the current angular position of the roller 2 is a prerequisite. After complete measurement of the roller surface, the results are combined to form a 3-D topographic surface description.
An additional task when treating rollers 2 is to detect untrue running errors in the region of the journal on which the roller 2 is mounted. If all the untrue running errors are eliminated on the grinding disk side, fluctuations which are caused by the bearing points of the roller 2 in the journal can theoretically also occur on the rear side. For such investigations it is possible to provide a further measuring system (which can be installed on the rear side of the roller) or direct measurement of the journal can be provided (not illustrated in more detail in the figures).
In the geometrically conducted grinding method which is preferred for the grinding device 1 according to the invention, the forward movement occurs on the basis of the referencing, in contrast to the force-controlled grinding method according to the prior art which is described above. For this purpose, at the start of a grinding step, wireless contact is carried out with the roller 2. The reference value which is defined in this way determines the grinding profile.
After the desired contour (true running/profile/embossing) has been reached, further processing steps such as polishing can take place by means of the grinding treatment. Here, the treatment is generally force-controlled. This applies specifically to additional components such as superfinishing devices. The known dynamic drives are in principle suitable for this.
The required high level of accuracy requires that the geometric conditions on the longitudinal carriage 15 be known precisely. This applies specifically to the position of the zero points of the measuring devices 16 and the orientation of the grinding axis in the local coordinate system K'. These values can be determined in advance, but precise determination of the position of the reference wire 14 is necessary in all cases before each new grinding process, said determination requiring external determination of the roller diameter at two axial positions which have to be defined.
This also applies to the case in which the wire attachments have actually not been changed since, for example, when the roller 2 was inserted into the bearing blocks 3, changes can take place to the geometry which can subsequently effect the grinding accuracy.
If, in particular, figures 7A and 8A are considered, the various adjustment possibilities of the individual components become apparent. The movement travel of an actuating device 25 is denoted by s, which actuating device 25 can regulate the inclination of the transverse carriage 18 on the basis of the values determined by the inclination sensor 23. This is desirable since the position of the axes of the roller 2 and tool 17 are preferably at the same height.
The radial forward movement in the x direction for the tool 17, which is regulated by the measuring probe 24, is carried out by a further actuating device 26 (see figures 7B and 8B). For this purpose, a continuous adjustment of the measured values r,,, and ud occurs (distance between the measuring probe 24 and the roller surface) compared to s,, (roller radius) . Adjustment of the attitude angle of the tool 17 is possible by means of the piezo-actuators 21, with the result that specific profiles and embossing can be generated.
The entire sequence is guided, monitored and evaluated in a program-controlled fashion. The regulation of the drives, the evaluation of the various sensors and safety precautions can be performed by a conventional NC controller which is known in principle or a motion controller.
With respect to the accuracy levels which can be achieved and which in conventional stationary grinding devices are determined exclusively by the geometric accuracy of the grinding bed, it is to be expected that the technical measuring assistance by means of referencing and scanning allows an equally high level of accuracy to be achieved in the treatment of the rollers 2 even though the foundations can be produced easily and simply.
The two sensing devices 22 or scanners 22, for example laser scanners, in the exemplary embodiment detect the reference wire 14 and permit, in conjunction with an inclination sensor 23, the position and direction of a local coordinate system K' on the transverse carriage 18 to be determined. The scanners 22 can be embodied here, as illustrated in figure 7A, on the transverse carriage 18, or, as is apparent from figure 8A, can be arranged in the longitudinal carriage 15. The selection can take place as desired in accordance with, for example, criteria of ease of operation, of protected arrangement, etc.
For the sensing of the surface of the roller 2 by means of a measuring probe 24, it is necessary to be able to adjust the measuring probe 24 in order to maintain the measuring range depending on the current size of the tool 17 (in the exemplary embodiment of the grinding disk) . This can be implemented in discrete steps since no change is necessary during the measuring process.
The spatial position of the measuring devices 16 with respect to the local system (K') either has to be known or can be determined from the current position of the movement axes. It is absolutely necessary to measure the longitudinal carriage 15 of the grinding device 1 in this respect.
In the illustrated exemplary embodiment, the measuring devices 16 comprise, as described, two scanners 22 and an inclination sensor 23, which are arranged on the transverse carriage 18 of the grinding device 1. This makes it possible to determine the position and orientation of the local coordinate system K' on the longitudinal carriage 15 in which the position of the measuring devices 16 and of the tool 17 are known.
During the treatment of the roller 2, the setpoint values for the forward movement are adapted on the basis of the determined deviations between the global coordinate systems K and the local coordinate system K'.
Conventionally already known measuring probes 24 are possible for the surface treatment. Inductive measuring probes 24, which have a high degree of accuracy (approximately 0.1 pm) and are suitable for all surfaces in question are usually already in use for this purpose. A disadvantage is their limited dynamics, for which reason under said circumstances the rotational speed of the roller has to be limited during measurement. Complete, uninterrupted measurement then takes a correspondingly long time. Alternatively, laser measurement systems can be applied which nowadays also permit mirrored surfaces to be measured. These operate in a contactless fashion and have now also achieved accuracy levels of approximately 0.2 pm. Mechanical systems for moving the measuring probe 24 can be dispensed with here because the measuring probe 24 does not have to be moved back during grinding, in contrast to an inductive measuring probe 24.
The measured value of the system with the results of the referencing and the fixed and known positions of the measuring devices 16 provide a measuring point on the roller surface expressed in a radius with respect to the roller axis. When the roller 2 is rotating, the measuring points can be set either during continuous axial movement of the longitudinal carriage 15 along the roller 2 longitudinally with respect to a helical line, or multiple rotations can be used to acquire measuring points during incremental movement. A
permanently available signal for the current angular position of the roller 2 is a prerequisite. After complete measurement of the roller surface, the results are combined to form a 3-D topographic surface description.
An additional task when treating rollers 2 is to detect untrue running errors in the region of the journal on which the roller 2 is mounted. If all the untrue running errors are eliminated on the grinding disk side, fluctuations which are caused by the bearing points of the roller 2 in the journal can theoretically also occur on the rear side. For such investigations it is possible to provide a further measuring system (which can be installed on the rear side of the roller) or direct measurement of the journal can be provided (not illustrated in more detail in the figures).
In the geometrically conducted grinding method which is preferred for the grinding device 1 according to the invention, the forward movement occurs on the basis of the referencing, in contrast to the force-controlled grinding method according to the prior art which is described above. For this purpose, at the start of a grinding step, wireless contact is carried out with the roller 2. The reference value which is defined in this way determines the grinding profile.
After the desired contour (true running/profile/embossing) has been reached, further processing steps such as polishing can take place by means of the grinding treatment. Here, the treatment is generally force-controlled. This applies specifically to additional components such as superfinishing devices. The known dynamic drives are in principle suitable for this.
The required high level of accuracy requires that the geometric conditions on the longitudinal carriage 15 be known precisely. This applies specifically to the position of the zero points of the measuring devices 16 and the orientation of the grinding axis in the local coordinate system K'. These values can be determined in advance, but precise determination of the position of the reference wire 14 is necessary in all cases before each new grinding process, said determination requiring external determination of the roller diameter at two axial positions which have to be defined.
This also applies to the case in which the wire attachments have actually not been changed since, for example, when the roller 2 was inserted into the bearing blocks 3, changes can take place to the geometry which can subsequently effect the grinding accuracy.
If, in particular, figures 7A and 8A are considered, the various adjustment possibilities of the individual components become apparent. The movement travel of an actuating device 25 is denoted by s, which actuating device 25 can regulate the inclination of the transverse carriage 18 on the basis of the values determined by the inclination sensor 23. This is desirable since the position of the axes of the roller 2 and tool 17 are preferably at the same height.
The radial forward movement in the x direction for the tool 17, which is regulated by the measuring probe 24, is carried out by a further actuating device 26 (see figures 7B and 8B). For this purpose, a continuous adjustment of the measured values r,,, and ud occurs (distance between the measuring probe 24 and the roller surface) compared to s,, (roller radius) . Adjustment of the attitude angle of the tool 17 is possible by means of the piezo-actuators 21, with the result that specific profiles and embossing can be generated.
The entire sequence is guided, monitored and evaluated in a program-controlled fashion. The regulation of the drives, the evaluation of the various sensors and safety precautions can be performed by a conventional NC controller which is known in principle or a motion controller.
With respect to the accuracy levels which can be achieved and which in conventional stationary grinding devices are determined exclusively by the geometric accuracy of the grinding bed, it is to be expected that the technical measuring assistance by means of referencing and scanning allows an equally high level of accuracy to be achieved in the treatment of the rollers 2 even though the foundations can be produced easily and simply.
Claims (30)
1. A grinding device (1) for the surface treatment of rollers (2), in particular rollers (2) for machines producing, finishing and/or treating webs, such as paper, cardboard or tissue machines, characterized in that the grinding device (1) comprises stationary components and mobile components which can be separated from one another, and wherein the stationary components comprise guide rails (5) which extend essentially parallel to a roller axis of the roller (2) which is to be treated and are connected to a substructure (6).
2. The grinding device as claimed in claim 1, characterized in that the guide rails (5) are connected directly to the substructure (6).
3. The grinding device as claimed in claim 1, characterized in that the guide rails (5) are connected to carriers (10) which are inserted into the substructure.
4. The grinding device as claimed in claim 1, characterized in that the guide rails (5) are connected to a frame (4) which is inserted into the substructure.
5. The grinding device as claimed in one of claims 1 to 4, characterized in that the roller (2) which is to be ground can be arranged on bearing blocks (3) which are connected to the substructure (6).
6. The grinding device as claimed in claim 6, characterized in that passive insulation against excitation of vibrations by the substructure (6) in the form of a damping layer (7) and/or damping elements in the form of spring elements is provided between the substructure (6) and the bearing blocks (3) and/or between the substructure (6) and the guide rails (5).
7. The grinding device as claimed in claim 5, characterized in that the bearing blocks (3) and/or the guide rails (5) have devices in the form of actuators (8) which can be open-loop and closed-loop controlled, for actively bringing about decoupling from the substructure (6).
8. The grinding device as claimed in one of claims 5 to 7, characterized in that bearing points (9a, 9b) of the roller (2) in the bearing blocks (3) can be adjusted horizontally and/or vertically.
9. The grinding device as claimed in one of claims 1 to 8, characterized in that the mobile components of the grinding device (1) comprise a longitudinal carriage (15) which is movably guided on the guide rails (5) and is arranged in such a way that it can be moved or slid along an extension direction (Z) of the roller axis of the roller (2) which is to be treated.
10. The grinding device as claimed in claim 9, characterized in that the longitudinal carriage (15) has bearings (11) which interact with the guide rails (5).
11. The grinding device as claimed in claim 10, characterized in that the bearings (11) are embodied as sliding bearings or roller bearings so as to form a fixed/freely moving bearing arrangement with recirculating roller shoes (12, 12a, 12b).
12. The grinding device as claimed in one of claims 9 to 11, characterized in that a transverse carriage (18) is arranged so as to be movable or slidable on the longitudinal carriage (15), wherein a movement direction (X) of the transverse carriage (18) is oriented essentially perpendicularly to the movement direction (Z) of the longitudinal carriage (15).
13. The grinding device as claimed in claim 12, characterized in that the transverse carriage (18) can be horizontally and/or vertically pivoted with respect to the longitudinal carriage (15).
14. The grinding device as claimed in claim 12 or 13, characterized in that a rail bearing system (19) is formed between the longitudinal carriage (15) and the transverse carriage (18), in particular a rail bearing system (19) in which bearings engage around guide rails.
15. The grinding device as claimed in one of claims 12 to 14, characterized in that the transverse carriage (18) is arranged in such a way that it is secured on the longitudinal carriage (15) or can be removed therefrom.
16. The grinding device as claimed in one of claims 12 to 15, characterized in that a tool (17), in particular a grinding disk, a belt grinder, a grooving device, a superfinishing device or a honing device can be arranged on the transverse carriage (18).
17. The grinding device as claimed in claim 16, characterized in that the tool (17) can be operated with geometry control.
18. The grinding device as claimed in one of claims 1 to 17, characterized in that the grinding device (1) has measuring devices (16) by means of which a position of the grinding device (1) relative to the roller (2) which is to be treated can be determined.
19. The grinding device as claimed in claim 18, characterized in that the measuring devices (16) comprise at least two sensing devices (22) for a reference object (14).
20. The grinding device as claimed in claim 19, characterized in that the sensing devices (22) are embodied in the form of scanners (22), in particular of laser scanners.
21. The grinding device as claimed in claim 19 or 20, characterized in that the reference object (14) is embodied in the form of a stretched wire (14), which wire (14) is arranged essentially parallel to the roller axis of the roller (2) which is to be treated and has a fixed, invariable geometric relationship with the roller axis.
22. The grinding device as claimed in claim 21, characterized in that the wire (14) is arranged in such a way that it can be sensed by the scanners (22).
23. The grinding device as claimed in claim 21 or 22, characterized in that the scanners (22) are arranged on the longitudinal carriage (15) or on the transverse carriage (18).
24. The grinding device as claimed in one of claims 18 to 23, characterized in that the measuring devices (16) comprise at least one inclination sensor (23) which is arranged on the transverse carriage (18) and by which an inclination of the transverse carriage (18) relative to the substructure (6) can be sensed.
25. The grinding device as claimed in one of claims 18 to 24, characterized in that the measuring devices (16) have at least one measuring probe (24) which is arranged on the transverse carriage (18) and by which the roller surface which is to be treated can be sensed and/or the distance between the grinding device (1) and the roller axis can be measured.
26. The grinding device as claimed in claim 25, characterized in that at least one further measuring probe is provided which is arranged opposite the first measuring probe (24) with respect to the roller axis, on a rear side of the roller (2), by means of which further measuring probe untrue running errors at the support points of the roller (2) can be sensed.
27. The grinding device as claimed in one of claims 18 to 26, characterized in that the measured values of the scanners (22), of the inclination sensor (23), of the at least one measuring probe (24) of the measuring devices (16) can be fed in for the purpose of performing open-loop and closed-loop control of the position of the tool (17) by means of actuating devices (21, 25, 26) which are embodied, in particular, in the form of piezo-actuators.
28. The grinding device as claimed in claim 27, characterized in that the tool (17) can be pivoted with respect to the roller axis in a plane which is predefined by the directions (x) and (z) by at least one actuating device (21).
29. The grinding device as claimed in claim 27 or 28, characterized in that the tool (17) can be pivoted with respect to the roller axis in a plane which is predefined by the directions (x) and (y) by at least one actuating device (25).
30. The grinding device as claimed in one of claims 27 to 29, characterized in that the tool (17) can be adjusted with respect to the roller axis in the direction (x) by at least one actuating device (26).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009003140.5 | 2009-05-15 | ||
| DE102009003140A DE102009003140A1 (en) | 2009-05-15 | 2009-05-15 | Grinding device for rolls |
| PCT/EP2010/055156 WO2010130531A1 (en) | 2009-05-15 | 2010-04-20 | Grinding device for rolls having stationary guide rails and mobile grinding unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2761841A1 true CA2761841A1 (en) | 2010-11-18 |
Family
ID=42315902
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2761841A Abandoned CA2761841A1 (en) | 2009-05-15 | 2010-04-20 | Grinding device for rollers |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20120122374A1 (en) |
| EP (1) | EP2429760A1 (en) |
| CN (1) | CN102458758A (en) |
| CA (1) | CA2761841A1 (en) |
| DE (1) | DE102009003140A1 (en) |
| WO (1) | WO2010130531A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113787387A (en) * | 2021-08-31 | 2021-12-14 | 常州大学 | Spinning machine rubber roll surface grinding and repairing device |
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| CN103264326B (en) * | 2013-06-09 | 2015-08-12 | 无锡立达纺织机械器材有限公司 | A kind of grinding attachment of bag licker-in grinder |
| CN103537961B (en) * | 2013-09-26 | 2016-06-29 | 青岛云路先进材料技术有限公司 | Roll surface treatment device for crystallizer |
| DE102014019481A1 (en) * | 2014-12-21 | 2016-06-23 | Icm - Institut Chemnitzer Maschinen- Und Anlagenbau E.V. | Device for finishing a non-rotating tube |
| US10052735B2 (en) * | 2015-06-24 | 2018-08-21 | Apko Technology, Inc. | In situ grinding apparatus for resurfacing rubber belts and rollers |
| CN105150036B (en) * | 2015-10-09 | 2017-12-19 | 河北工业大学 | A kind of grinding carriage mobile battery pole piece roll grinder |
| CN106217177B (en) * | 2016-08-25 | 2018-06-05 | 东莞市华邦精密模具有限公司 | A kind of mold mosaic block sanding apparatus |
| CN106271955B (en) * | 2016-08-30 | 2017-07-28 | 江苏同庆车辆配件有限公司 | A kind of annular workpieces lapping device in railway freight-car |
| CN110000639A (en) * | 2019-04-26 | 2019-07-12 | 合肥工业大学 | A kind of roller diameter based on roll grinder and taper on-position measure device and measurement method |
| DE102021001408A1 (en) | 2021-03-17 | 2022-09-22 | Kemal Arslan | grinding mount |
| DE202021001002U1 (en) | 2021-03-17 | 2021-09-30 | Kemal Arslan | Grinding holder |
| CN113263439B (en) * | 2021-06-07 | 2022-07-19 | 厦门大学 | Intelligent carrying tool for large-caliber optical elements |
| CN113601346B (en) * | 2021-09-06 | 2023-05-23 | 东莞兆泰机械设备有限公司 | Online polishing equipment for roller |
| CN116021354B (en) * | 2023-02-21 | 2023-06-23 | 长沙迈科轴承有限公司 | Bearing protruding grinding machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE391525C (en) * | 1924-03-07 | Lorenz Blum | Transportable device for regrinding and polishing rolls that have become out of round, especially drying cylinders in paper machines | |
| FR1298429A (en) * | 1961-05-30 | 1962-07-13 | Machine for grinding and checking measurements for large volume rotating parts | |
| DE1502423B2 (en) * | 1964-11-17 | 1972-03-30 | Farrel Corp., Ansonia, Conn. (V.StA.) | DEVICE FOR ALIGNING A ROLLER ON A ROLLER GRINDING MACHINE |
| US3653162A (en) * | 1971-01-25 | 1972-04-04 | Ingersoll Milling Machine Co | Apparatus for turning workpieces |
| US4077163A (en) * | 1976-07-28 | 1978-03-07 | Usm Corporation | Pivot mechanism for grinding wheel infeed |
| US4712332A (en) * | 1982-11-30 | 1987-12-15 | Energy Adaptive Grinding, Inc. | Centerless and center-type grinding system |
| DE9209844U1 (en) * | 1992-07-22 | 1992-11-12 | J.M. Voith Gmbh, 7920 Heidenheim | Device for machining the outer surface of a cylinder within a paper machine |
| DE4304478A1 (en) * | 1993-02-15 | 1994-08-18 | Pagendarm Gmbh | Application device |
| DE19542387C1 (en) * | 1995-11-01 | 1997-06-19 | Mannesmann Ag | Device for regrinding the rolls installed in roll stands |
| DE29915022U1 (en) * | 1999-08-27 | 1999-10-21 | Schmötzer, Hubert, 74653 Ingelfingen | Device for the material-removing processing of the lateral surface of cylindrical rollers of a printing press |
| US6200204B1 (en) * | 1999-09-17 | 2001-03-13 | Voith Sulzer Paper Technology North America, Inc. | Roll grinder with vibration dampening |
| US6802759B1 (en) | 1999-12-31 | 2004-10-12 | Voith Paper Holding Gmbh | Grinder |
| CN1182941C (en) * | 2000-11-30 | 2005-01-05 | 钱远强 | On-site grinding polisher |
| DE102004013031A1 (en) | 2004-03-16 | 2005-10-06 | Waldrich Siegen Werkzeugmaschinen Gmbh | Method and machine for producing a roll |
| CN200977604Y (en) * | 2006-11-02 | 2007-11-21 | 福裕事业股份有限公司 | Machine body structure for door shaped processor |
| CN101195178B (en) * | 2007-12-19 | 2010-04-14 | 哈尔滨工业大学 | Gantry type ultra-precise fly miller |
-
2009
- 2009-05-15 DE DE102009003140A patent/DE102009003140A1/en not_active Withdrawn
-
2010
- 2010-04-20 WO PCT/EP2010/055156 patent/WO2010130531A1/en active Application Filing
- 2010-04-20 EP EP10714882A patent/EP2429760A1/en not_active Withdrawn
- 2010-04-20 CA CA2761841A patent/CA2761841A1/en not_active Abandoned
- 2010-04-20 CN CN2010800317242A patent/CN102458758A/en active Pending
-
2011
- 2011-11-15 US US13/296,954 patent/US20120122374A1/en not_active Abandoned
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113787387A (en) * | 2021-08-31 | 2021-12-14 | 常州大学 | Spinning machine rubber roll surface grinding and repairing device |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2010130531A1 (en) | 2010-11-18 |
| EP2429760A1 (en) | 2012-03-21 |
| US20120122374A1 (en) | 2012-05-17 |
| CN102458758A (en) | 2012-05-16 |
| DE102009003140A1 (en) | 2010-11-18 |
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| Date | Code | Title | Description |
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| FZDE | Discontinued |
Effective date: 20150422 |